Web winding



M y 4, 1954 J. P. LOCKE 2,677,508

WEB WINDING Filed June 19, 1950 3 Sheets-Sheet l J. P. LOCKE May 4, 1954 WEB WINDING 3 Sheets-Sheet 2 Filed June 19, 1950 .vzlll y 4, 1954 J. P. LOCKE 2,677,508

WEB WINDING Filed June 19, 1950 5 Sheets-$heet 5 FIG.5.

FORCE IN ROLL. DIAMETER IN INCHES Patented May 4, 1954 i wen WINDING:

40 111 -I ock Univ rs City, e s emr ts Bernie B rojr Bag-Company, St; Louis} Mala-corporatien-ofiM-isi'souri Annl QatiQn-Ju s a se ame-1 9st News 1';

his at o tstsso w t izi' di e, an more parti u a lyto w b nders h f if ct en drum type.

h Q is t ztthe in ent n isms ro si n of a twmd-rnmtfriction drum winder: for winding a webs into a roll awith v close .control over the n s f-thsr ll. and-- ada te o i d a o l orsubsta tiallt uni o m hardn ss h teue sut s ma from its. innermost o: t rm s se volution According to -my: observations, the hardnessioi'" a roll of webimateriallwound. by a friction drum winder is for the most part dtermined'by the compressive force exerted ..upon the web along; a line transverse to; the le gth of the web' in the niptof the web rollheingwound andthe' drum of the winder where the web first comes on to the web r011, tas sum ingthat' the Webis being wound under substantiallyeonstant ten sion. This is particularly trueof web'material that has a relatively. low modulus of elasticity in tension. I believe th'atthe hardnessfof the roll is largely determinedin the easeof such material by-thecompression of'the web material being wound against the drum ofthe winder where the materialffirst comes on to the roll. The extent ofncompression, of course, is dependent upon the compressiveforee exerted'on the web by theweb .1'0111' To wind. at web" roll of uniform hardness, it should be snostantially equally compressedthroughout'its length; For equal compression... of the Web throughout its length, the compressive force exertedon the web by the-web roll should be maintained substantialby constant throughout the-windin flperation,

The invention, in generaLflinvolve's a friction drum winder having. a rider roll' bearing onth'e web r011 'beinghwound, and means for applying" force to theweb' r011 'as'the latter is'woundin accordance with its increasein diameter insuch manner as tomaintain thejcompre'ssive force exerted 'on the web in" the nip ofthe'webroll and the drum of the'wi'nder wherethe webfirst winds on to the roll substantially constant throughout the wmdinenoperation; This pin duces a web roll 'of substantially uniform" ha'rd nessfromits innermpstto its outermost con, volution.

The force iswappliedt-to theweb r011 beingwound by fl id pr s urem ans a n 1-1 1 is r ll for i -sineit t ard e Webl nd sel p sd wit luid unde pre su hrsush a l n ine asine a pres ure- OMM W i e h s s 3: tro l d bwmsn mmabk he W t el it inemap es in diam t r for-veryins the pressure p -tfiid' r s u eme ns? s indin s sss is ms ma sis' or sm h al e ineuoh a wa as to, v ry th p su 's uid sms" f uid erss ur m s h h' m ultem" force exerted-by the, wet; roll 'against the frietion r m) o etamm iqmp v i srs on:

b b be s thi e o l and. h rict o rum abs fin ll instan This" mea m be ad s i h estt m s th v lv inethsr yswhs s e en uniis ardns si hs web-W 1 i clssirs -f e were; a s a i tmtss of csns iu ti n' h c sduse 7 its re red, llfi Q room to a minimum and allow. for the'use'oi s ng e u d er ssu s'ms ns' Whi assur n parallelism i h' rid :9 and f Q semn ther iatu fss W111i 'petta ea s sn i s tlpeintsd qathsrsm itsh The n sn ien s sotqihn c mp ses. he" 3 m e s n fs mh nstiqn sf sismst e s of s si stis nd, a wi l be exem l ed in 1 's. wstut f si ins tsr described; and the sqope r the a plication of In t se tem n ive i hs ssible s l trates 4 s. 'visw n svatien 9 fris isn' stem w nner 0? :1; il ustratin ps tsin' hs. nesiti n he steam" a the star o windin 3.,

sm ss ms l o the n ntisn of Fi pene ating p m the pps, they occupy whens q l is smu halt W0 H s s vi w'illu trstins p @111 sl p th eramma ea ly 111 F g: s a we ital s ctisn keiqn'i e i -4* f hiegli and;

R e 1s aera hill strs i ssrtsi fsrseewsb' ee s ins s a iss 8' an iihs rums as here n i lust ated-are f. ua met ant near the bottom of the latter with their ages erai fietne s me sriaeet lp sns smi s a esiistae s sqmswhls gre er han ths 4. mm tha he e is? a sRscs be we he nesm ntsfoi ber s'whish i srslss 'SQQUQR as; d e-1 i we we fri sri drum 1 3 hav n -s af 59nd! humans at th ir ans 3 a e dtiv n hssams direction (counterclockwise as viewed in Fig. 2) and are adapted peripherally to support and drive a web roll R (shown about half wound in phantom in Fig. 2) being wound on an arbor I3. The web being wound is designated W and comes on to the web roll in the nip of the web roll and the friction drum I of the winder, which is hereinafter referred to as the first drum of the winder, the drum 3 being hereinafter referred to as the second drum of the winder. The web W, coming on to the periphery of the web roll R, is com pressed against the first friction drum I by the Web roll.

The compressive force to which the web is subjected is represented by the force arrow or vector F in Figs. 2 and 3. This force is exerted downward in the direction of the line joining the centers of the web roll and the first drum I. The

magnitude of the vector F depends upon the diameter of the web roll and the downward force applied to the top of the web roll by a rider roll I5, which may be positively biased downward by fluid pressure means generally designated I1. It will be seen that as the diameter of the web roll increases in winding, the weight of the web roll I increases, the angle of the direction of vector F with respect to the vertical changes, and the point of application of the vector also changes. The magnitude of vector F is the algebraic sum of the resultant of the weight of the web roll (and arbor) in the direction of the vector and the resultant of the force applied by the rider roll in the direction of the vector.

Referring now to Fig. 5, which is a graph in which the horizontal coordinates represent roll Y diameter in inches and the vertical coordinates represent force in pounds, the curve A represents the total vertical force which must result from V the weight of the web roll (and arbor) and the vertical force due to the rider roll to produce a vector F of constant magnitude in a specific case involving a winder wherein drums I and 3 are /2 inches in diameter with their axes spaced apart 11% inches, and wherein the web being wound weighs about 0.44 lb. per yard of its length. The curve A is plotted by selecting a desired magnitude for vector F (this being about 260 lbs. for thecurve A illustrated) and determining the total vertical force acting directly downward in the line of the center of the web roll necessary to establish this vector magnitude for the various vector angles. For example, the total vertical force acting through the center of the web roll necessary to produce a magnitude for vector F of 260 lbs. when the diameter of the web roll is 2 inches v When the diameter of the web is about 230 lbs. roll is 12 inches, the total vertical force required to produce a 260 lb. vector F is about 450 lbs. When the diameter of the Web roll is 36 inches (full roll diameter), the total vertical force required to produce a 260 lb. vector F is about 510 lbs.

The curve B represents the dead weight of the web roll (plus the weight of the arbor I3). For example, when the diameter of the web roll is 2 inches, its weight plus the arbor weight is about 10 lbs. When the diameter of the web roll is 12 inches, its weight plus the arbor weight is about 50 lbs. When the diameter of the web roll is 36 inches (full roll), its weight plus the arbor weight is about 440 lbs.

The curved C represents the combined dead weights of the web roll, arbor, and the rider roll (including elements which add dead weight to the rider roll), and thus represents the total dead formed. in the side frames 9 and I I.

- as indicated at 29.

weight contributing toward the vector F. This curve is drawn for a rider roll dead weight of about 70 lbs., and is plotted simply by adding 70 lbs. to the vertical coordinates of curve B. Thus, at 2 inch roll diameter, the total dead weight is lbs., at 12 inch roll diameter the total dead weight is lbs., and at 36 inch full roll diameter the total dead weight is 510 lbs. 1 I

The curve D represents the extra downward vertical force which must be applied to the rider roll to augment the dead weight of the web roll, arbor, and rider roll to produce the desired magnitude of 260 lbs. for the vector F. This curve is determined by plotting the differences between the vertical coordinates of curves A and C. Thus it will be seen that when the diameter of the web roll is 2 inches, the rider roll must apply an extra force of about lbs. (the difference between the 230 lbs. and 80 lbs. vertical ordinates of curves A and C at 2 inch roll diameter). When the diameter of the web roll is 12 inches, the rider roll must apply an extra force of about 330 lbs. (the difference between the 450 lb. and 120 lb. vertical ordinates of curves A and C at 12 inch roll diameter). When the diameter of the web roll is 36 inches, no extra force is required of the rider roll, other than its own weight. The 260 lb. magnitude for vector F is purposely selected so that at the full roll diameter of 36 inches, no extra force need be applied to the rider roll.

The rider roll I5 bears on the top of the web roll and is adapted to move upward as the web roll increases in diameter while its axis is maintaincd parallel to the axes of the first and second friction drums and the web roll, and directly above the axis of the web roll. For this purpose, the rider roll is provided at its ends with trunnions IS and H which are journalled in bearings 23 vertically slidable in vertical guideways 25 The vertical plane of the guideways is'centered with respect to the aXes of the drums I and 3. Racks 27 extend vertically upward from the bearings 23, being fixed at their lower ends to the bearings The teeth of the racks face toward the right as viewed in Fig. 2. A shaft or torque bar 3| is journallecl at its ends in the side frames 9 and IE adjacent the upper ends of the frames and has pinions 33 fixed thereon in mesh with the racks. The axis or" the bar 3| parallels the axes of the friction drums I and 3. The arrangement is such that the ends of the rider roll are constrained against relative vertical movement, while being free to move upward (or downward), so that the rider roll remains parallel to the friction drums as the web roll R increases in diameter and moves the rider roll upward.

The fluid pressure means I? comprises an air pressure cylinder 35 mounted in vertical position on the outer side of the side frame II. A piston 31 slides in the cylinder and a piston rod 39 extends from the piston through the upper head of the cylinder to a connection at 4| with the upper end of the adjacent rack 27. In Fig. 3, the connection 4| is diagrammatically shown as made to the rider roll bearing rather than to the upper end of the rack as in Figs. 1 and 2 for simplification of illustration. The cylinder has a pressure supply port 43 at its upper end and a vent port 45 at its lower end. The arrangement is such that by supplying air under pressure to the cylinder above the piston through port 43, the piston will tend to pull down the adjacent rack 21 and thus tend to bias the rider roll I5 downward against the top of the web roll R. The downward force aerated Goinn'iercialiy a'va i bie -pressure regulator with some modification to adapt it-fo'r use iii-the Winder or thisihl'rfitl611 shownin Fig-s; valve to in" general" comprises agenerally cupshapedbo'dy it. he peirside or" tliebouy is closed by rsiii'e t hragirr 53; thema r m or the diaphragm'beirig' compressed against the rim or the body by abonn-et ssholt'e'o tothe body.- Withhrthe body; between-thediaphra mand a baffle plate 51", ls'a chamber 59: The baiile plate 2 isheld a'gainstashoulder BPbya'head 63 011 setting st whien extendsthrough an op'eninginthe center" of thbaflie pie-teens which is threaded at-its left endas viewea ih'Fig'i 3 in the base of the body 5|. Within the-body Si between the bailie pl-at'" 51*andthe base of the body is anothercham-ber 615 The latter isof smaller diameter than thechamten 59 toprovide -the shoulder 5|;

The-fitting 65 hasa axial passage 69 which narrows down at its right-end as viewed iii-Fig. 3,- and-radio? poi'ts H providing for communication betweenthepass'ag'e as and-the cnambers1; At its left end: as viewed iriFiga 3j-the-fitting opens into a transverseair inletpassage 73 in the base of thebody 5i. Br ttle-center attire-diaphragm 5 3 isaveht 9-5-5 -This-is adapted to-be clos'edby a ball-end valve Ti axially shda-ble'ih thenar-row right end of the passage Sh-through thentting: 65; The valve has ahead I'd-located in the'airinlet passage 13-. A" strainer soreeri- B-lsu-I' mund's-the head. Aspring 83% eac t's ag iiist thc' headfrom plug 85 thr'eaded an'opening irrthebas'e of the body 5| aligned vli-th 'the fitting 65 to bias the Valve- Ti toward seating: engagement w'ith -thevent Thebody 51 1 foi ziie'd with an air outlet passage 8? leading from thohamber 51. A sy-- phon tube 89 in -the baffle plate 51 providesfor communication" hetw'eerichamber 59 amrthe 'aii" outlet passage. A follower rod 9l is 'slidable in the end or the bonnet 55.- Atits inner end this rod carries a spring seat 93. Abompressionspring 95 reacts-from the seat 93- againsta seat 9'5 e ging the diaphragm 53 to bias the diaphr a ,m toward the left as viewed in Fig. 3. Inthe wall of the bonnet are breather holes 98.

-The spring 95 norm-ally holds the parts in the position shown in -Fig, 3' wherein'the ball end of the valve 11 closes the vent 15; The valve 11 is held against the bias of spring 83 iii-the retracted position illustrated inlFig. 3" wnereinthevalve head 19 is spaced to the left of'the adjacent end of the fitting" 55. Un' der'these circumstances; air mayflow through theinlet passage 13 through the passage 69 in the fittingt65,-through the radial ports H in'the fitting to thechamb'er 61 and thence through 'th'e oui'ilei'ipassage 81-:a'nd line in to the cylinder, with apressurewdrop in flowing through-thevalve; The chamber 59 is in communication: with chamber G-Lthrough the tub-ese, so that the diaphragm sa-issubjec'ted to thepressiirein the outlet; a lirwhich i'saenerally" the same as in the cylinder 35. this pressure should become high enoiigl i to overoome the force of spring ';-fo'r a particularsettntg ofvithis spring, th'ediap agmimcves away fi' orri the-bal l end of valve Wand \iente'd throughthevent- T5 the bonhet ut throu the breather: he s- 991 'l nis ventmg occurs after the valve 11* has moved to the right Riga. to a forward position where e' headws on the valve closes: he thereby-blocking; ort 'the: passage win-the fitting from the flair in liifiipassagi' 3% Wheri-the pressiirehas-been selffiei'ently' rediicedg fispi ing 95= :returns thel ports to the :Fig. s positionzliovs iiiuoh pressure the w 1 49' willf hold the cylinder is: determined ameter of thawed-roll inareases. mneconsists oi anelohg'ate -flat-bar' formed with a cantedge 103 engaging a rollower rollen' 1 05 on the outer end of the-follower rodtl. The cam: edge, asillustrated is ofl such development-and so phased as-to adjust thehohtrdlfialve to -obtain the diiierent airr pressures" required iir-the' aircylinder 35 at dilferent web roll diametcrs to supply the extraforce whicmmust'be applied to the rider-roll tomaintain the magnitude of force" F at'least substantiallyconstant throughout the winding. The necessary developmentof thecam edge may be: determined item: the curve B and the characteristics of. the valvel Itwill berseenv that the development of theeam is such that itfirst gradually movestherodfil inward. thereby gradually to increase: the pressure held in the cylinder '3 5",: and ultimately 'permits the rod i 91- to move outwardthereby 'gradually to lower the pressure held in: the cylinder; l

The friction "drums land 3a nd-theiriderroll l5 are all positively driven in counterclockwise direction by gearingillustratediin Eigse land 4. As shown, this i gearing comprises a horizontal shaft 1 01 journalld in the side frames il -andt I. Fixed on-this shaft outward oftheside frame- 9' isargear its in mesh with gears IH and' lit-on drum shafts 5 and 1, respectively Shaft lifl has a pulley ll5-fi xed on-its outer -end driven through a belt drive from a. suitable source of power (not shown). A-riderroll drivesh-aft- H1 is-moun-ted invertical position on the outside'of side frame-9 by-means of upper and lower bearings HQand I21: This'shaft H1 extends gener'ally the 'full height of theside frame with its axisinters'ecting the axis oithe rider roll. A bevel gear-"i Z3 onthehorizontal shaft llllmeshes with a; bevel gear l-24 on the lower'end ofthe shaft 11-! to drivethelatter. Thatru'hnion [9 of the rider roll I5 extends out of its bearing" 23" and has a bvelgear ['25 fixe'don its outer end. This meshes with'a bevel gear [21 which rotates with the shaft "I ll but'which is axially slidable thereon. The gear l Zi'i'scarried by ayoke I23 fixed to the bearing 23-for the rider roll trimnion 19 It is keyed to rotate with theshaft -I ll while being axially'slidable thereon by providing it'- witha key slidable in a spline l3'I- in theshaft I ll. At I33 are shown bearings for engaging the ends ofthe shaft I 35 of the 'arbora 'l hese bearings are slidable in the guideways 25 below the bearings 23.

Operation is as follows:

Air is supplied to the air inlet of the pressure control valve 49 at a pressure high enough to accommodate the highest pressure needed in the cylinder 35, taking into account the pressure drop in the valve. At the start of winding, the rider roll 15 is in its lowermost position bearing down on the arbor l3 and wedging it between the first and second friction drums l and 3. Racks 21, cam l! and the piston 31 are in their lowermost position. The cam ml under these circumstances holds the follower rod 9| in such position that the valve 49 regulates the pressure in cylinder 35 to such value as to exert the necessary extra force on the rider roll l5 to make force F equal the desired value (260 lbs. for example). Referring to Fig. 5, it will be seen that for a 2 inch roll diameter in the particular case illustrated, this extra force would be 150 lbs., and the cam is so developed and phased as, in its position corresponding to 2 inch roll diameter, to set the valve to establish such a value of pressure in the cylinder 35 as to produce 150 lbs. force.

As winding proceeds, the web roll R, increasing in diameter, moves the rider roll l5, racks 21 and cam l0! upward. As the cam moves upward from starting position, it moves the follower rod 9| inward, thus gradually increasing the pressure in the cylinder 35 to increase the extra force exerted by the rider roll on the web roll in accordance with the requirements as dictated by the curve D of Fig. 5. For example, when the diameter of the web roll has increased to 12 inches, the cam ID! has moved the follower rod 9| to a position wherein valve 49 establishes such pressure in the cylinder 35 as to cause an extra force of 330 lbs. to be applied by the rider roll to the web roll. From this point on, however, the follower rod 9| moves outward, thereby gradually decreasing the pressure in the cylinder 35 to decrease the extra force exerted by the rider roll on the web roll in accordance with the requirements dictated by the curve D of Fig. 5. For example, when the diameter of the web roll has increased to 36 inches, the cam meanwhile has permitted the follower to move outward completely to relieve the spring 95, so that the space in cylinder 35 above the piston 37 is fully vented, with the result that no extra force is applied by the rider roll.

It will be understood that instead of maintaining the force F substantially constant to wind rolls of uniform hardness, the force might be A varied as desired by changing the development of the cam l0l. Or a particular cam might be retained and the entire curve D shifted up or down as by changingthe length of the rod 9|. Thus, the winder of this invention is useful not only to carry out the method of this invention for producing rolls of uniform hardness but also to control the roll hardness in any manner desired.

The winder construction involving the gearing together of the racks 21 by the torque bar 3| and pinions 33 thereon and the use of only one air cylinder is advantageous in that it assures parallelism of the rider roll 15 to the friction drums l and 3 throughout the winding even though only one air cylinder at one side of the winder is used without requiring the use of special anti-backlash gears and racks to eliminate play.

In view of the above, it will be seen that the several objects of the invention are achieved and other advantageous results attained.

As many changes could be made in the above constructions without departing from the scope of the invention, it is intended that all matter contained in the above description or shown in the accompanying drawings shall be interpreted as illustrative and not in a limiting sense.

I claim:

1. A friction drum winder comprising two friction drums journalled at their ends in side frames near the bottom of the frames, a rider roll journalled at its ends in bearings which are vertically slidable in vertical guideways in the side frames, the rider roll being adapted to bear on the top of a web roll being wound and to be moved upward by the web roll as the latter increases in diameter, racks extending vertically upward from the rider roll bearings, a torque bar journalled at its ends in the side frames near the top of the frames and carrying pim'ons in mesh with the racks, a fluid pressure cylinder mounted in vertical position on one of the side frames having an inlet port at its upper end and a vent at its lower end, a piston reciprocable in the cylinder, and a piston rod extending from the piston through the upper end of the cylinder and fixed to the upper end of the adjacent rack.

2. A friction drum winder comprising two friction drums journalled at their ends in side frames near the bottom of the frames, a rider roll journalled at its ends in bearings which are vertically slidable in vertical guideways in the side frames, the rider roll being adapted to bear on the top of a web roll being wound and to be moved upward by the web roll as the latter increases in diameter, racks extending vertically upward from the rider roll bearings, a torque bar journalled at its ends in the side frames near the top of the frames and carrying pinions in mesh with the racks, a fluid pressure cylinder mounted in vertical position on one of the side frames having an inlet port at its upper end and a vent at its lower end, a piston reciprocable in the cylinder, a piston rod extending from the piston through the upper end of the cylinder and fixed to the upper end of the adjacent rack, means for supplying fluid under pressure to the inlet port of the cylinder including a pressure control valve for variably controlling the pressure of fluid in the cylinder above the piston, and means movable with the rider roll for controlling the valve.

3. A friction drum winder comprising two friction drums journalled at their ends side frames near the bottom of the frames, a rider roll journalled at its ends in bearings which are vertically slidable in vertical guideways in the side frames, the rider roll being adapted to bear on the top of a web roll being wound and to be moved upward by the web roll as the latter increases in diameter, racks extending vertically upward from the rider roll bearings, a torque bar journalled at its ends in the side frames near the top of the frames and carrying pinions in mesh with the racks, a fluid pressure cylinder mounted in vertical position on one of the side frames having an inlet port at its upper end and a vent at its lower end, a piston reciprocable in the cylinder, and a piston rod extending from the piston through the upper end of the cylinder and fixed to the upper end of the adjacent rack, means for supplying fluid under pressure to the inlet port of the cylinder including a pressure control valve for variably controlling the pressure of fluid in the cylinder above the piston, said valve being mounted on one of said side frames and having a movable pressure-setting element, and a cam mounted on the adjacent rack and acting on the pressure-setting element of the valve for varying the pressure of fluid in the cylinder above the piston as winding progresses.

4. A friction drum Winder as set forth in claim 3 wherein the cam is formed gradually to increase the pressure of fluid in the winder above the piston from the start of winding to a maximum, and then gradually to decrease the pressure to a minimum.

References Cited in the file of this patent UNITED STATES PATENTS Number Name Date 1,967,922 Cameron July 24, 1934 2,194,078 Simonds Mar. 19, 1940 2,196,000 Richardson Apr. 2, 1940 

